CN85107943A - Vehicle acceleration-controlled system - Google Patents
Vehicle acceleration-controlled system Download PDFInfo
- Publication number
- CN85107943A CN85107943A CN198585107943A CN85107943A CN85107943A CN 85107943 A CN85107943 A CN 85107943A CN 198585107943 A CN198585107943 A CN 198585107943A CN 85107943 A CN85107943 A CN 85107943A CN 85107943 A CN85107943 A CN 85107943A
- Authority
- CN
- China
- Prior art keywords
- mentioned
- operational ton
- torque
- toric transmission
- output
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Withdrawn
Links
- 230000001133 acceleration Effects 0.000 title claims abstract description 24
- 230000005540 biological transmission Effects 0.000 claims abstract description 35
- 238000001514 detection method Methods 0.000 claims abstract description 13
- 238000013459 approach Methods 0.000 claims description 3
- 230000000694 effects Effects 0.000 description 5
- 230000001105 regulatory effect Effects 0.000 description 5
- 239000004519 grease Substances 0.000 description 4
- 239000012530 fluid Substances 0.000 description 2
- 239000011159 matrix material Substances 0.000 description 2
- 230000000630 rising effect Effects 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000000881 depressing effect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 238000002347 injection Methods 0.000 description 1
- 239000007924 injection Substances 0.000 description 1
- 239000006200 vaporizer Substances 0.000 description 1
Images
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W10/00—Conjoint control of vehicle sub-units of different type or different function
- B60W10/04—Conjoint control of vehicle sub-units of different type or different function including control of propulsion units
- B60W10/06—Conjoint control of vehicle sub-units of different type or different function including control of propulsion units including control of combustion engines
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W10/00—Conjoint control of vehicle sub-units of different type or different function
- B60W10/04—Conjoint control of vehicle sub-units of different type or different function including control of propulsion units
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W10/00—Conjoint control of vehicle sub-units of different type or different function
- B60W10/10—Conjoint control of vehicle sub-units of different type or different function including control of change-speed gearings
- B60W10/101—Infinitely variable gearings
- B60W10/103—Infinitely variable gearings of fluid type
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W30/00—Purposes of road vehicle drive control systems not related to the control of a particular sub-unit, e.g. of systems using conjoint control of vehicle sub-units
- B60W30/18—Propelling the vehicle
- B60W30/188—Controlling power parameters of the driveline, e.g. determining the required power
- B60W30/1884—Avoiding stall or overspeed of the engine
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
- B60Y2400/00—Special features of vehicle units
- B60Y2400/30—Sensors
- B60Y2400/307—Torque sensors
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Mechanical Engineering (AREA)
- Automation & Control Theory (AREA)
- Control Of Vehicle Engines Or Engines For Specific Uses (AREA)
- Control Of Driving Devices And Active Controlling Of Vehicle (AREA)
- Control Of Fluid Gearings (AREA)
- Auxiliary Drives, Propulsion Controls, And Safety Devices (AREA)
- Control Of Transmission Device (AREA)
Abstract
The present invention relates to be applicable to the acceleration-controlled system of the power actuated vehicle that toric transmission is housed.Characteristics of the present invention are as follows: when the driver excessive to the added operational ton of acceleration pedal, the output torque that makes toric transmission surpasses maximum permissible value and when ascendant trend occurring, this phenomenon can be detected by torque detection means, and utilize the operational ton correction mechanism to be revised, make to be lower than the practical operation amount by the operational ton that the operational ton transmission mechanism transmits to the engine control operating side from above-mentioned acceleration pedal.Therefore, the present invention can be controlled at the horsepower output of driving engine in the suitable scope, and the output torque of above-mentioned toric transmission is reduced to below the above-mentioned maximum permissible value.
Description
The present invention relates to be applicable to the acceleration-controlled system of the power actuated vehicle that toric transmission is housed.
Along with the development of high efficiency oil pressure pump/motor, the so-called hydraulic actuator (HST) that is formed by this pump and motor combination and the performance of fluid mechanics driving device (HMT) have significantly improved.Therefore, also adopt the opportunity of this toric transmission ripe gradually at the aspects such as automobile that require higher efficiency.
But the advantage of this change-speed box is to be to start under the infinitely-great state at reduction ratio, on principle, no longer needs power-transfer clutch and torque converter.If the toric transmission with this specific character intactly is used in the past automobile, be easy to generate fault when quickening after the starting so.That is to say that the reduction ratio of above-mentioned change-speed box approaches infinitely great state during owing to starting, so if the driver adopts too quicklyly to acceleration pedal, the torque of adhesion wheel will be excessive so, be easy to skid between wheel and the road surface, thereby cause racing of the engine.
The objective of the invention is to solve effectively such problem, promptly control under the situation that adopts above-mentioned toric transmission in the vehicle of engine output, be easy to generate the problem of tyre slip and racing of the engine during starting at driver's step on the accelerator.
Characteristics of the present invention are: in order to achieve the above object, adopted structure shown in Figure 1.That is to say, the characteristics of acceleration-controlled system of the present invention are: this control system is applicable to the vehicle that has with lower member, be the driving engine 1 that horsepower output changes along with being added in the operational ton on the engine control operating side, 2 pairs of added operational tons of acceleration pedal of driver are delivered to the operational ton transmission mechanism of using on the above-mentioned engine control operating side 3; Be positioned to adhesion wheel 4 and transmit on the circuit 5 of above-mentioned engine output, when starting, can be transferred to infinity to reduction ratio or approach infinitely-great toric transmission 6; And have following special mechanism, promptly detect the torque detection means 21 of the output torque of above-mentioned toric transmission 6; When utilizing these torque detection means 21 detected output torques to surpass predetermined maximum permissible value, surpass amount in order to offset it, the operational ton that is delivered to by aforesaid operations amount transmission mechanism 3 on the above-mentioned engine control operating side is exported the operational ton correction mechanism 22 that reduces correction.And the effect of above-mentioned torque detection means 21 is the physical quantitys of taking out the torque that is equivalent to above-mentioned toric transmission 6 outputs; And the effect of aforesaid operations amount correction mechanism 22 to be output torque value that above-mentioned torque detection means 21 is taken out and predetermined maximum allow torque value to compare, and it surpassed carry out inverse feedback after amount is amplified.
Owing to adopt said structure, so it is excessive to work as 2 pairs of added operational tons of acceleration pedal of driver, the output torque that makes toric transmission 6 surpasses maximum permissible value and during the trend that occurs rising, this phenomenon can be detected by torque detection means 21, and utilize operational ton correction mechanism 22 to be revised, make to be lower than the practical operation amount by the operational ton that operational ton transmission mechanism 3 transmits to the engine control operating side from above-mentioned acceleration pedal.As a result, the horsepower output of driving engine 1 is controlled in the suitable scope, and the output torque of above-mentioned toric transmission 6 is reduced to below the above-mentioned maximum permissible value.
Below with reference to Fig. 2 one embodiment of the present of invention are described.
Fig. 2 is the system specialization figure of acceleration-controlled system of the present invention when being used for automobile.This automobile has with lower member, i.e. the driving engine 1 that changes along with being added in the operational ton on the engine control operating side of horsepower output; 2 pairs of added operational tons of acceleration pedal of driver are delivered to the operational ton transmission mechanism of using on the above-mentioned engine control operating side 3; Be positioned to adhesion wheel 4 and transmit on the route 5 of horsepower output of above-mentioned driving engine 1, when starting, can be transferred to infinitely-great toric transmission 6 to reduction ratio.Specifically, above-mentioned driving engine is the engine petrol with carburetter 7, and motion arm 8b is contained on the fulcrum 8a of flow regulating valve 8 of above-mentioned carburetter 7, and it is equivalent to above-mentioned engine control operating side.In addition, aforesaid operations amount transmission mechanism 3 has following part: the moving rod 11 that moves forward and backward along with the trampling operation of acceleration pedal 9; The dwang 13 that rotates around fulcrum 12 along with the advance and retreat action of this moving rod 11; The link rod 14 that connects the motion arm 8b of the rotation section of this dwang 13 and above-mentioned flow regulating valve 8.Moreover, above-mentioned toric transmission 6 is a kind of hydraulic gears, it has following two oil pressure pump/motors: one is the 1st capacity-variable type oil pressure pump/motor 15 on being connected the output shaft of above-mentioned driving engine 1, and another is the 2nd capacity-variable type oil pressure pump/motor 16 that is connected on the above-mentioned adhesion wheel 4.Inflow and outflow mouth 15a, the 15b of above-mentioned oil pressure pump/motor 15 and inflow and outflow mouth 16a, the 16b of above-mentioned oil pressure pump/motor 16 couple together by oil pipe circuit 17,18.
In addition, in this automobile, torque detection means 21 and operational ton correction mechanism 22 are housed, the former is used to detect the output torque of above-mentioned toric transmission 6, the latter is when utilizing these torque detection means 21 detected output torques to surpass predetermined maximum permissible value, surpass amount in order to offset it, the operational ton on the motion arm 8b that is delivered to above-mentioned flow regulating valve 8 by aforesaid operations amount transmission mechanism 3 is exported to reduce revise.Oil pressure when specifically, above-mentioned torque detection means 21 takes out car acceleration by pilot conduits 23 in the oil hydraulic circuit of above-mentioned toric transmission 6 mesohigh sides (for example, the oil pressure in the above-mentioned pipeline 18).That is to say, because the oil pressure value in the high pressure side oil hydraulic circuit of this toric transmission 6 is corresponding with the output torque of change-speed box 6, so take out the physical quantity that this oil pressure value can be used as the above-mentioned output torque of expression.On the other hand, operational ton correction mechanism 22 utilizes the output of single-acting formula oil hydraulic cylinder device 24 to bring in the fulcrum 12 that supports above-mentioned dwang 13, and make this oil hydraulic cylinder device 24 carry out work, thereby the position of the above-mentioned fulcrum 12 of scalable by the oil pressure that is taken out by above-mentioned Oil Guide pipeline 23.Its details is as follows: above-mentioned oil hydraulic cylinder device 24 has following part, and promptly the matrix end is contained in oil cylinder 26 on the permanent seat 25 by pivot; Be contained in the piston 27 that can slide in the oil cylinder 26, stretch out from piston 27, its end reaches the exterior piston rod 28 of oil cylinder 26; Make the spring 29 of above-mentioned piston 27 to piston rod 28 direction of retreat effects.Above-mentioned fulcrum 12 is arranged on the end of above-mentioned piston rod 28.And draw grease chamber 31 in the formation of the matrix end of above-mentioned oil cylinder 26, this draws the grease chamber and can enlarge accordingly according to the slip effect of above-mentioned piston 27 or dwindle.Above-mentioned Oil Guide pipeline 23 is connected this and draws in the grease chamber 31.Above-mentioned spring 29 is the more coil springs of the number of turns, and its set condition is as described below, promptly corresponding to necessarily the depressing in advance of output torque maximum permissible value, above-mentioned piston 27 is remained on the last position of falling back.
The following describes the action of this embodiment.
When parking of automobile, for example, when the capacity of the oil pressure pump/motor 15 of toric transmission 6 was zero, the capacity of another oil pressure pump/motor 16 was a maxim, and the power of driving engine 1 can not transmit to adhesion wheel 4.That is to say that the reduction ratio of above-mentioned toric transmission 6 is infinitely great.Bend the throttle 9 can improve the horsepower output of driving engine 1 under this state, increases the capacity of above-mentioned oil pressure pump/motor 15 simultaneously gradually, hastens thereby can start and add this automobile.Can utilize microcomputer, as incoming signal reduction ratio be controlled with the speed of a motor vehicle, throttle valve position etc.In addition, when when starting, if above-mentioned acceleration pedal 9 to trample operational ton excessive, acceleration-controlled system of the present invention is just started working.That is to say, when to above-mentioned acceleration pedal 9 to trample operational ton more suitable, when the output torque of above-mentioned toric transmission 6 was lower than the maximum permissible value of setting, the oil pressure that is taken out by above-mentioned Oil Guide pipeline 23 also can correspondingly reduce.Therefore, the piston 27 of oil hydraulic cylinder device 24 can remain under the precompressed effect of spring 29 on the last position of falling back, be that the stopping projection 27a of piston 27 remains on the contacted position of aft bulkhead 26a with oil cylinder 26, the fulcrum 12 of dwang 13 is set on the position of regulation.But, if to above-mentioned acceleration pedal 9 to trample operational ton excessive, the output torque of above-mentioned change-speed box 6 continues to rise after surpassing above-mentioned maximum permissible value, then the piston thrusts that oil pressure produced of drawing in the grease chamber 31 by the above-mentioned oil hydraulic cylinder device 24 of above-mentioned Oil Guide pipeline 23 introducings surpass the precompressed of above-mentioned spring 29, and (left among the figure) moves thereby make piston 27 begin forwards.And, this piston 27 all the way move forward to application force that thrust that above-mentioned oil pressure produces and above-mentioned spring 29 produced mutually steadily the time till.As a result, the fulcrum 12 of above-mentioned dwang 13 leaves the afore mentioned rules position and forwards moves, thereby the operational ton that transmits to the motion arm 8b of above-mentioned carburetter 7 from above-mentioned acceleration pedal 9 is reduced and revises.In addition, the actuating quantity with the corresponding oil hydraulic cylinder device 24 of above-mentioned oil pressure variable quantity is to adjust by the spring constant of suitable selection spring 29.Yet the spring constant of above-mentioned spring is set in such scope in this system, promptly can obtain offsetting by the action of oil hydraulic cylinder device 24 to the amount that surpasses of the maximum permissible value of above-mentioned output torque.Therefore,, still can be controlled at the operational ton that is delivered on the aforesaid operations arm 8b in the suitable scope, the output torque of above-mentioned change-speed box 6 is reduced to below the maximum permissible value although excessive to the tread-on quantity of acceleration pedal 9.Therefore, in this case, even when starting step on the accelerator too quickly a bit, can not produce yet and skid between excessive, above-mentioned adhesion wheel 4 of output torque and the road surface and phenomenon such as racing of the engine.
In the above-described embodiment, illustrated that the present invention is used for being equipped with the situation of the vehicle of vaporizer gasoline engine.Certainly, the present invention is not limited only to this purposes, and is applicable to the vehicle that gasoline engine jet and diesel motor etc. are housed too.Yet for injection-type engine, the electric terminal that the noticeable degree of fuel injector is used will become the engine control operating side.And for the vehicle that adopts diesel motor, the control stalk that control fuel-injection pump regulating mechanism is used will become the engine control operating side.
In addition, the structure of toric transmission also is not limited only to above-mentioned a kind of certainly, also can adopt above-mentioned fluid mechanics driving device (HMT).
Moreover, torque master also is not limited only to a kind of of the foregoing description certainly, also can adopt so-called torque sensor etc., its principle of work is: the feature detection such as elastic displacement by member go out to act on the torque on the toric transmission output shaft, and it is transformed into electric signal.
In addition, it is mechanical that the operational ton correction mechanism also is not limited only to above-mentioned oil pressure, can also adopt electric apparatus formula or electrical oil pressure type.And, when being used for injection-type engine, also can adopt complete electric.
The present invention can provide so a kind of vehicle acceleration-controlled system, and this system is owing to adopted said structure, and (this speed changer is rising so can very simply and reliably eliminate the employing buncher Can make speed reducing ratio reach infinitely great when moving) time fault that produces easily, it is excessive namely to export torque, tyre slip, the race of engine.
Fig. 1 is a structure instruction diagram of the present invention;
Fig. 2 is the system specialization figure of the embodiment of the invention.Among the figure:
The 1-driving engine.
2-driver
3-operational ton transmission system
The 4-adhesion wheel
The 5-transmission line
The 6-toric transmission
8b-engine control operating side (motion arm of flow regulating valve)
The 9-acceleration pedal
The 21-torque detection means
22-operational ton correction mechanism
Claims (1)
- Vehicle acceleration-controlled system is applicable to the vehicle that has with lower member, i.e. the driving engine that changes along with being added in the operational ton on the engine control operating side of horsepower output; The driver is delivered to the operational ton transmission mechanism of using on the above-mentioned engine control operating side to the added operational ton of acceleration pedal; Be positioned to adhesion wheel and transmit on the route of above-mentioned engine output, when starting, can be transferred to reduction ratio infinity or approach infinitely-great toric transmission; It is characterized by torque detection means and when utilizing this torque detection means to detect output torque when surpassing the maximum permissible value of being scheduled to the output torque that detects above-mentioned toric transmission, surpass amount in order to offset it, the operational ton that is delivered to by aforesaid operations amount transmission mechanism on the above-mentioned engine control operating side is exported the operational ton correction mechanism that reduces correction.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP228798/84 | 1984-10-29 | ||
| JP59228798A JPH0623019B2 (en) | 1984-10-29 | 1984-10-29 | Vehicle acceleration control device |
| JP228798 | 1984-10-29 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN85107943A true CN85107943A (en) | 1986-07-23 |
| CN85107943B CN85107943B (en) | 1988-08-17 |
Family
ID=16882017
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN85107943A Expired CN85107943B (en) | 1984-10-29 | 1985-10-28 | Vehicle acceleration-controlled system |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US4716788A (en) |
| EP (1) | EP0180184B1 (en) |
| JP (1) | JPH0623019B2 (en) |
| KR (1) | KR900003946B1 (en) |
| CN (1) | CN85107943B (en) |
| DE (1) | DE3569911D1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102483109A (en) * | 2009-09-14 | 2012-05-30 | 斯堪尼亚商用车有限公司 | Method and system for control of a clutch |
Families Citing this family (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2518210B2 (en) * | 1986-06-11 | 1996-07-24 | 株式会社島津製作所 | Acceleration adjuster in hydraulic drive system |
| US4838124A (en) * | 1986-06-30 | 1989-06-13 | Toyota Jidosha Kabushiki Kaisha | System for integrally controlling automatic transmission and engine |
| JPH0545534Y2 (en) * | 1987-12-16 | 1993-11-22 | ||
| JPH0678051B2 (en) * | 1988-08-31 | 1994-10-05 | 株式会社クボタ | Work vehicle speed controller |
| JPH0341252A (en) * | 1989-07-06 | 1991-02-21 | Mazda Motor Corp | Controller for vehicle equipped with continuously variable transmission |
| JP3011339B2 (en) * | 1990-03-30 | 2000-02-21 | マツダ株式会社 | Output reduction control device for engine with automatic transmission |
| JP2636520B2 (en) * | 1991-01-23 | 1997-07-30 | 日産自動車株式会社 | Control device for continuously variable transmission |
| JP3155027B2 (en) * | 1991-05-20 | 2001-04-09 | ジヤトコ・トランステクノロジー株式会社 | Transmission control device for automatic transmission |
| JP2001280175A (en) * | 2000-03-30 | 2001-10-10 | Hitachi Ltd | Device and method for controlling automatic transmission using gear-type mechanism |
| DE50008351D1 (en) * | 2000-11-25 | 2004-11-25 | Ford Global Tech Inc | Efficiency improvement in CVT transmissions by avoiding slippage achieved by torque control using an electrical machine |
| JP4770309B2 (en) * | 2005-07-19 | 2011-09-14 | 日産自動車株式会社 | Vehicle engine output control device |
| DE112007001662A5 (en) * | 2006-08-09 | 2009-04-23 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Method and device for limiting the input torque of a belt pulley belt transmission with integrated hydromechanical torque sensing device |
Family Cites Families (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CH412593A (en) * | 1961-08-17 | 1966-04-30 | Doorne S Automobielfabriek N V | Motor vehicle with a carburetor engine and a V-belt transmission |
| BE630364A (en) * | 1962-06-29 | |||
| GB1045278A (en) * | 1962-09-26 | 1966-10-12 | Dowty Hydraulic Units Ltd | Power transmission |
| DE2301776B2 (en) * | 1973-01-15 | 1976-12-02 | P.I.V. Antrieb Werner Reimers Kg, 6380 Bad Homburg | CONTROL DEVICE FOR A TRAVEL DRIVE CONSISTING OF A COMBUSTION ENGINE AND MOTOR AND A CONTINUOUSLY ADJUSTABLE ACCESSORY DRIVE DRIVEN BY THESE |
| DE2340841C2 (en) * | 1973-08-13 | 1982-03-25 | Robert Bosch Gmbh, 7000 Stuttgart | Device for the common automatic control of a drive unit consisting of an internal combustion engine and a transmission |
| US4383456A (en) * | 1975-09-25 | 1983-05-17 | Ganoung David P | Apparatus using a continuously variable ratio transmission to improve fuel economy |
| US4342298A (en) * | 1979-03-14 | 1982-08-03 | Ganoung David P | Engine and transmission control apparatus |
| NL165821C (en) * | 1976-02-09 | 1981-05-15 | Doornes Transmissie Bv | INFLATABLE VARIABLE TRANSMISSION. |
| US4232572A (en) * | 1978-07-17 | 1980-11-11 | Sundstrand Corporation | Engine-transmission control system |
| US4515041A (en) * | 1980-05-21 | 1985-05-07 | Aisin Seiki Kabushiki Kaisha | Control system and method for a power delivery system having a continuously variable ratio transmission |
| JPS5846837U (en) * | 1981-09-28 | 1983-03-29 | 日野自動車株式会社 | Automotive engine control device |
| DE3151351C2 (en) * | 1981-12-24 | 1995-04-13 | Man Technologie Gmbh | Motor vehicle drive unit with a control device |
| US4444286A (en) * | 1982-05-13 | 1984-04-24 | Sundstrand Corporation | Torque-control with overspeed regulation and method of controlling a hydrostatic drive |
| US4458560A (en) * | 1982-05-21 | 1984-07-10 | Aisin Seiki Kabushiki Kaisha | Control system and method for a power delivery system having a continuously variable ratio transmission |
| US4458561A (en) * | 1982-05-21 | 1984-07-10 | Frank Andrew A | Control system and method for a power delivery system having a continuously variable ratio transmission |
-
1984
- 1984-10-29 JP JP59228798A patent/JPH0623019B2/en not_active Expired - Lifetime
-
1985
- 1985-10-19 KR KR1019850007734A patent/KR900003946B1/en not_active IP Right Cessation
- 1985-10-28 DE DE8585113698T patent/DE3569911D1/en not_active Expired
- 1985-10-28 CN CN85107943A patent/CN85107943B/en not_active Expired
- 1985-10-28 EP EP85113698A patent/EP0180184B1/en not_active Expired
- 1985-10-28 US US06/792,294 patent/US4716788A/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102483109A (en) * | 2009-09-14 | 2012-05-30 | 斯堪尼亚商用车有限公司 | Method and system for control of a clutch |
Also Published As
| Publication number | Publication date |
|---|---|
| EP0180184A1 (en) | 1986-05-07 |
| JPH0623019B2 (en) | 1994-03-30 |
| EP0180184B1 (en) | 1989-05-03 |
| CN85107943B (en) | 1988-08-17 |
| KR900003946B1 (en) | 1990-06-05 |
| US4716788A (en) | 1988-01-05 |
| KR860003126A (en) | 1986-05-21 |
| JPS61105230A (en) | 1986-05-23 |
| DE3569911D1 (en) | 1989-06-08 |
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